JP2004346823A - Valve gear for internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve gear capable of improving the lubricating performance by forcibly supplying the lubricant to a pivot part of a locker arm and a link rod, and a pivot part of the link rod and an oscillating cam. <P>SOLUTION: The torque of a driving cam 5 is transmitted to the oscillating cam 7 through the link arm 14, the locker arm 13 and the link rod 15 to open and close each intake valve 2, and the valve lift of the intake valve is variably controlled by the rotation of a control shaft 17 and a control cam 18. A lubricant reserving part 22 is formed on an upper end part of a cylinder head 1, recessed parts 12 are formed on both sides of an upper face side of the oscillating cam, and the lubricant collected in the recessed parts from the lubricant reserving part is splashed up in oscillating the oscillating cam, to forcibly supply the lubricant to the direction of a pin 20 and to supply the lubricant to a pin 21 side through an outer face of the oscillating cam. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a valve train for an internal combustion engine, and more particularly to a valve train for an internal combustion engine capable of improving the lubrication performance of a pivot portion at a connection point between a swing cam and a transmission mechanism.
[0002]
[Prior art]
As a conventional valve operating device for an internal combustion engine of this type, there is one having a variable mechanism for changing a valve lift and an operating angle of an intake valve or an exhaust valve in accordance with an engine operating state. Some are described in patent documents.
[0003]
In brief, this valve operating device is applied to a device having two intake valves per cylinder, and has a shaft centered on the outer periphery of a drive shaft that rotates synchronously with the rotation of a crankshaft. A drive cam eccentric from the center is fixedly provided, and a cylindrical camshaft is rotatably provided coaxially on the outer periphery of the drive shaft.
[0004]
This camshaft is integrally provided with a pair of left and right swing cams corresponding to a pair of intake valves at both ends, and the rotational force of the driving cam is provided with a multi-node link transmission mechanism on both swing cams. Via the valve lifter to open and close each intake valve.
[0005]
The transmission mechanism is disposed above the swing cam, and is rocker arm swingably supported by a control cam fixed to a control shaft, one end of which is rotatably linked to the drive cam and the other end of which is rotatably connected to the drive cam. A link arm rotatably connected to one end of the rocker arm, and one end rotatably connected to the other end of the rocker arm, and the other end rotatably connected to the tip of the cam nose of the one swing cam. And a linked link rod.
[0006]
When the drive cam rotates eccentrically with the rotation of the drive shaft, the rocker arm swings around the control cam as a fulcrum via the link arm, and the swing motion of the rocker arm becomes a linear motion. After the conversion, the swing cam is swung about the drive shaft as a fulcrum. Thus, the cam surface on the lower surface of the swing cam opens and closes both intake valves via the valve lifter.
[0007]
Further, the control shaft is eccentrically rotated by the forward / reverse rotation control of the control shaft according to the change in the engine operation state, thereby changing the rocking fulcrum of the rocker arm. Thereby, the contact position of the cam surface of each swing cam with respect to the upper surface of each valve lifter changes, and the valve lift amount and operating angle of each intake valve are variably controlled. As a result, it is possible to improve the fuel efficiency and the like when the engine is running at a low speed and the output torque when the engine is running at a high speed, and to sufficiently bring out the engine performance.
[0008]
[Patent Document 1]
JP-A-2002-303108
[Problems to be solved by the invention]
By the way, in the conventional valve gear, the rocking cam is rocked by a rocker arm or a link rod against a large friction caused by a spring force of a valve spring or the like. A large frictional resistance is generated in a first pivot portion which is a connection portion between the swing cam and the link rod and a second pivot portion which is a connection portion between the rocker arm and the link rod.
[0010]
However, since no positive lubrication means has been taken for the first and second pivot portions, the lubrication performance of these pivot portions is insufficient. In particular, since the second pivot portion is located sufficiently above the oscillating cam, lubricating oil scattered by the valve gear is not sufficiently applied to the second pivot portion, so that lubricity is reduced.
[0011]
As a result, in order to ensure durability, the rocker arm, the link rod, and the pivot pin constituting the second pivot portion must be formed of a wear-resistant and expensive material.
[0012]
[Means for Solving the Problems]
The present invention has been devised in view of the actual situation of the conventional valve operating device, and the invention according to claim 1 has, in particular, an arrangement in which the oil is provided at a predetermined position within a range in which the swing cam of the cylinder head swings. A reservoir is provided, wherein the lubricating oil in the oil reservoir adhering to the rocking cam is flipped up toward the pivot when the rocking cam rocks.
[0013]
According to the present invention, the lubricating oil in the oil reservoir is jumped up with the swing of the swing cam, and the lubricating oil can be directly supplied to the pivot, so that the lubricating performance of the pivot can be improved. Is improved.
[0014]
Therefore, a smooth operation of the transmission mechanism and the swing cam can be obtained at all times, and the occurrence of wear and the like of the pivot portion can be prevented, and the durability can be improved.
[0015]
As a result, it is not necessary to form the transmission mechanism and the pivot portion with an expensive wear-resistant material, and it is possible to suppress a rise in cost.
[0016]
The invention according to claim 2 is characterized in that the swing cam is arranged so that the tip of the cam nose is immersed in the oil reservoir when the engine valve is lifted to the maximum.
[0017]
According to the present invention, as a specific operation, when the swing cam swings, the lubricating oil of the oil reservoir adheres to the tip of the cam nose portion and jumps up toward the pivot portion via the swing power as it is. , Lubricating oil is supplied directly to the pivot.
[0018]
Therefore, the lubrication performance of the pivot portion is improved, and the same operation and effect as in claim 1 can be obtained.
[0019]
According to a third aspect of the present invention, the upper surface of the swing cam on the side of the cam nose is formed flat, and when the swing cam swings, the lubricating oil in the oil reservoir is scooped up by the flat upper surface. It is characterized by having comprised in.
[0020]
According to the present invention, since the lubricating oil in the oil reservoir is more actively scooped by the flat upper surface of the swing cam, more lubricating oil can be supplied to the pivot. .
[0021]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment of a valve train for an internal combustion engine according to the present invention will be described in detail with reference to the drawings. The valve train of this embodiment is applied to an internal combustion engine having two intake valves per cylinder and a variable mechanism for varying the valve lift of each intake valve according to the engine operating state.
[0022]
That is, as shown in FIGS. 1 to 3, the valve train includes a pair of intake valves 2 and 2 slidably provided on a cylinder head 1 via a valve guide (not shown), A drive shaft 3 which is an internal hollow support shaft, a cam shaft 4 which is disposed for each cylinder, and is rotatably supported coaxially on an outer peripheral surface of the drive shaft 3, And a drive cam 5 fixed at a predetermined position, and provided integrally with both ends of the camshaft 4 and slidably in contact with valve lifters 6 and 6 provided at the upper ends of the intake valves 2 and 2, respectively. A pair of oscillating cams 7, 7 for opening each of the intake valves 2, 2 is linked to the driving cam 5 and the oscillating cams 7, 7, and the rotational force of the driving cam 5 is used for the oscillating cams 7, 2. A transmission mechanism 8 for transmitting the oscillating power (valve opening force) of the transmission 7, a control mechanism 9 for varying the operating position of the transmission mechanism 8, It is provided.
[0023]
The intake valves 2, 2 are moved in the closing direction by valve springs 10, 10 elastically mounted between the bottom of a substantially cylindrical bore housed in the upper end of the cylinder head 1 and a spring retainer at the upper end of the valve stem. Being energized.
[0024]
The drive shaft 3 is arranged along the front-rear direction of the engine, and both ends are rotatably supported by bearings (not shown) provided on the upper part of the cylinder head 1 and are provided at one end. The rotational force is transmitted from the crankshaft of the engine via an external driven sprocket, a timing chain wound around the driven sprocket, and the like, and the rotation direction is set in the direction of the arrow in FIG.
[0025]
Each of the camshafts 4 is formed in a substantially cylindrical shape along the axial direction of the drive shaft 3, and a shaft hole rotatably supported on the outer peripheral surface of the drive shaft 3 is formed in the inner axial direction. At the same time, a large-diameter cylindrical journal portion 4a formed at the center position is rotatably supported by a cam bearing (not shown).
[0026]
The drive cam 5 is formed in a substantially disk shape, and as shown in FIG. 3, a fixing tubular portion 5a is integrally provided on one side thereof, and the tubular portion 5a is Is fixed on the drive shaft 3 via a fixing pin 11 at a predetermined position in the axial direction, the outer peripheral surface 5b is formed in an eccentric cam profile, and the axis Y is the axis X of the drive shaft 3. Is offset by a predetermined amount in the radial direction.
[0027]
Each of the rocking cams 7 has a substantially raindrop shape of the same shape as shown in FIGS. 1, 2 and 4, and has a base end side centered on the axis X of the drive shaft 3 via the camshaft 4. In addition to the swinging cam, a cam surface 7a is formed on the lower surface of the swinging cam 7, and a base circular surface on the base end side and an arc shape from the base circular surface to the cam nose portions 7b, 7b. And a lift surface extending from the ramp surface to a top surface of a maximum lift provided on the distal end side of the cam nose portion 7b. The base circle surface and the ramp surface, the lift surface, and the top surface are formed by: The upper surface of each valve lifter 6 comes into contact with a predetermined position in accordance with the swing position of the swing cam 7.
[0028]
Further, a pin hole 7c through which a pin 21, which is a second pivot supporting portion connected to the other end portion 15b of the link rod 15 described later, is inserted through the cam nose portion 7b side of the swing cam 7 in a direction toward both side surfaces. Have been. Further, corrugated concave portions 12, 12 are formed on both upper side surfaces of each swing cam 7, respectively.
[0029]
As shown in FIGS. 1 to 3, the transmission mechanism 8 includes a rocker arm 13 disposed above the drive shaft 3, a link arm 14 for linking one end 13 a of the rocker arm 13 to the drive cam 5, 13 is provided with a link rod 15 for linking the other end 13b of the thirteen and the cam nose part 7b of the one swing cam 7.
[0030]
The rocker arm 13 has a support hole 13c formed in the center of the cylindrical base portion so as to penetrate from the lateral direction, and is swingably supported by a control cam 18 to be described later via the support hole 13c. One end 13a extending from the outer end of the cylindrical base has a pin 19 integrally protruding from the side of the tip, while the other end 13a extending from the inner end of the cylindrical base. 13b is formed with a pin hole into which a pin 20 which is a first pivot supporting portion connected to one end 15a of the link rod 15 is fitted inside the distal end portion.
[0031]
The link arm 14 includes a relatively large-diameter annular portion 14a and a protruding end 14b protruding at a predetermined position on an outer peripheral surface of the annular portion 14a. A fitting hole 14c rotatably fitted to the outer peripheral surface 5b of the driving cam 5 is formed, while a pin hole 14d through which the pin 19 is rotatably inserted is formed through the protruding end 14b.
[0032]
The link rod 15 is formed integrally by press molding, has a central portion formed in a substantially U-shaped cross section, and has an inner side bent in a substantially U-shaped shape in order to achieve compactness. Both ends 15a and 15b are rotatably connected to the other end 13b of the rocker arm 13 and the cam nose 7b of the swing cam 7 via the pins 20 and 21.
[0033]
That is, the link rod 15 is disposed substantially vertically, and one end 15a on the upper end is rotatably linked to the other end 13b of the rocker arm 13 by the pin 20 while the other end 15b on the lower end is The cam nose portion 7b of one swing cam 7 is rotatably linked to the swing cam 7 by a pin 21 inserted through the pin hole 7c.
[0034]
Each of the pins 20 and 21 is formed of a normal iron-based metal, and both ends thereof are press-fitted and fixed to pin holes 15c and 15d of both ends 15a and 15b of the link rod 15, and the pins of the rocker arm 13 are fixed. The pin hole of the other end 13b and the pin hole 7c of the swing cam 7 are slidably held.
[0035]
As shown in FIGS. 1 to 3, the control mechanism 9 includes a control shaft 17 rotatably supported by a bearing (not shown) disposed above the drive shaft 3, and an integral part of an outer periphery of the control shaft 17. And a control cam 18 fixed to the rocker arm and serving as a swing fulcrum of the rocker arm 13.
[0036]
The control shaft 17 is disposed in the engine front-rear direction in parallel with the drive shaft 3, and is controlled within a predetermined rotation angle range via a gear mechanism by an unillustrated electric actuator (DC motor) provided at one end. The rotation is controlled. On the other hand, the control cam 18 has a cylindrical shape, and the position of the axis P1 is deviated by a predetermined amount from the axis P2 of the control shaft 17 by the thickness.
[0037]
The electric actuator is driven by a control signal from a controller (not shown) that detects the operating state of the engine. This controller has a built-in microcomputer, a crank angle sensor, an air flow meter, and a water temperature sensor. Further, based on detection signals from various sensors such as a potentiometer for detecting the rotational position of the control shaft 17, the current engine operation state is detected by calculation or the like, and a control signal is output to the electric actuator.
[0038]
In this embodiment, as shown in FIG. 1, at a predetermined position at the upper end of the cylinder head 1, that is, at the upper end of the range in which the swing cam 7 swings, oil lubricating oil O is stored inside. A reservoir 22 is formed.
[0039]
More specifically, the oil reservoir 22 is formed at the upper end side of the holding holes 1a and 1a that slidably hold the valve lifters 6 and 6 of the cylinder head 1, and has a horizontal size. The swing cams 7 are formed so as to be larger than the width between the two swing cams 7, and the depth is set so that each swing cam 7 swings to lift each intake valve 2, 2 via the valve lifter 6 to the maximum. In this case, each cam nose portion 7b is formed so as to be immersed in the lubricating oil O inside.
[0040]
The oil reservoir 22 is supplied with lubricating oil flowing through first and second oil passages 23 and 24 formed inside the drive shaft 3 and inside the control shaft 17. I have.
[0041]
That is, the first oil passage 23 formed along the internal axial direction of the drive shaft 3 is formed in the radial hole 23a of the drive shaft 3 and the cam journal 4a of the camshaft 4 corresponding to the radial hole 23a. The lubricating oil which has communicated with the communication hole 25 formed along the radial direction lubricates the outer peripheral surface of the cam journal 4a and the inner peripheral surface of the bearing bracket (not shown) by flowing out of the lubricating oil. The liquid is dropped into the reservoir 22.
[0042]
The second oil passage 24 formed along the inner axial direction of the control shaft 17 is formed along the radial hole 17a of the control shaft 17 and the radial direction of the control cam 18 coaxially with the radial hole 17a. The lubricating oil flowing out of the communication hole 26 drips into the oil reservoir 22 by lubricating the control cam 18 and the inner peripheral surface of the support hole of the rocker arm 13. I have.
[0043]
Therefore, the lubricating oil is always stored in the oil reservoir 22 up to the predetermined liquid level L.
[0044]
In the following, the operation of the variable mechanism in the present embodiment will be briefly described. At the time of low-lift control, the control shaft 17 is driven to rotate in one direction via the electric actuator by a control signal from the controller. For this reason, the control cam 18 has its thick portion pivoted in one direction with respect to the control shaft 17 and is held at this rotational angle position. Accordingly, the one end 13a of the rocker arm 13 moves downward with respect to the control shaft 17, and the other end 13b rotates upward. For this reason, each of the swing cams 7 is forcibly pulled up on the cam nose portion 7b side via the link rod 15, and the whole swings in the direction toward the base end.
[0045]
Therefore, when the drive cam 5 rotates and the link arm 14 pushes up the one end 13a of the rocker arm 13, the lift amount is transmitted to the swing cam 7 and the valve lifter 6 via the link rod 15, but the lift amount is Becomes sufficiently small.
[0046]
Therefore, the valve lift of the intake valves 2 and 2 is reduced, the opening timing is delayed, and the valve overlap with the exhaust valve is reduced. For this reason, for example, improvement in fuel efficiency in a low load region and stable rotation of the engine can be obtained.
[0047]
On the other hand, during the high-lift control, the control shaft 17 is driven to rotate in the other direction by the electric actuator according to the control signal from the controller. Therefore, the control shaft 17 rotates the control cam 18 to the predetermined rotation angle position, and moves the thick portion downward. As a result, the one end 13a of the rocker arm 13 moves upward, and the other end 13b moves downward to push the cam nose 7b of the swing cam 7 downward via the link rod 15, thereby causing the swing cam to move. The whole 7 is turned to the cam nose part 7b side.
[0048]
Therefore, the contact position of each cam surface 7c of each swing cam 7 with respect to the upper surface 6a of each valve lifter 6 moves toward the cam nose portion 7b. For this reason, when the drive cam 5 rotates and pushes up one end 13 a of the rocker arm 13 via the link arm 14, the lift amount of the valve lifter 6 with respect to the valve lifter 6 increases.
[0049]
Therefore, the valve lift of each intake valve 2 increases, so that the opening timing is advanced and the closing timing is delayed. As a result, for example, the intake charge efficiency in a high load region is improved, and a sufficient output can be secured.
[0050]
Next, the lubricating action around the pins 20 and 21 in this embodiment will be described.
[0051]
That is, when each of the swing cams 7 swings during the operation of the above-described engine, the lubricating oil in the oil reservoir 22 is jumped up by the cam nose portion 7b, and the lubricating oil is transferred to the pin 20 or the pin hole side. Can be supplied directly to Therefore, the lubrication performance around the pin 20 is improved.
[0052]
In particular, when the cam nose portion 7b is immersed in the oil reservoir 22, lubricating oil is effectively collected in the concave portions 12, 12 on both sides, and the inside of the concave portions 12, 12 applied when the swing cams 7, 7 are flipped up. The lubricating oil is jumped up toward the pin 20. Therefore, a large amount of lubricating oil is directly supplied around the pin 20, and the lubrication performance around the pin 20 is further improved.
[0053]
At the same time, the lubricating oil in the recesses 12 and 12 and the lubricating oil adhering to the cam nose portion 7b travel along the outer surface of the swing cams 7 and 7 and are also supplied around the pin 21. Also improves the lubrication performance.
[0054]
Therefore, the smooth operation of the rocker arm 13 and the link rod 15 and the link rod 15 and the swing cam can be always performed smoothly together with the good lubricity around the transmission mechanism 8 by the lubricating oil from the first oil passage 23. At the same time, the occurrence of wear and the like around the pins 20 and 21 can be prevented, and the durability can be improved.
[0055]
As a result, it is not necessary to form the rocker arm 13, the link rod 15, and the pins 20, 21 with an expensive wear-resistant material, and it is possible to suppress an increase in cost.
[0056]
Further, the lubricating oil in the oil reservoir 22 is constantly supplied between the outer peripheral surfaces of the valve lifters 6 and 6 and the inner peripheral surfaces of the holding holes 1a and 1a. Lubrication performance is also greatly improved.
[0057]
FIG. 5 shows the oscillating cams 7, 7 used in the second embodiment of the present invention, and a recess 27 for collecting lubricating oil is formed on the upper surface 7d of the oscillating cams 7, 7 on the cam nose 7b side. It was done. Other configurations are the same as those of the first embodiment.
[0058]
Therefore, in this embodiment, the lubricating oil in the oil reservoir 22 is effectively collected in the concave portion 27 when the swing cams 7 and 7 swing as described above, so that the same as in the first embodiment. Effects can be obtained. In addition, since the concave portion 27 is simply formed on the upper surface 7d of the swing cams 7, 7, the forming operation of the concave portion 27 is easy, and it is possible to prevent a reduction in the forming operation efficiency.
[0059]
FIG. 6 shows a further different example, in which concave portions 28, 28 for collecting lubricating oil are formed on both side surfaces on the tip end side of the cam nose portion 7b so as to be substantially parallel to the upper surface 7d. Each of the recesses 28, 28 has an opening 28a on the tip side. Other configurations are the same as those of the first embodiment.
[0060]
Therefore, in this embodiment, the lubricating oil in the oil reservoir 22 can be effectively collected in the two recesses 28, 28, and the openings 28a, 28a are further formed at the distal end. Since the lubricating oil in the recesses 28, 28 can be flipped up from the openings 28a, 28a toward the pins 20 when the swing cams 7, 7 are flipped up, more lubricating oil can be efficiently turned around the pins 20. It becomes possible to supply well.
[0061]
FIG. 7 shows a further different example, in which convex portions 29, 29 are provided on the opposite side surfaces on the tip side of the cam nose portion 7b.
[0062]
Therefore, the lubricating oil adheres to the outer surface and the step surface of each of the convex portions 29, 29 in the oil reservoir 22, and the lubricating oil is flipped up toward the pin 20 to be supplied. Is obtained.
[0063]
FIG. 8 shows a still further example, in which a trapping hole 30 which is a communicating part communicating with the pin hole 7c is formed in the tip of the cam nose part 7b. The trapping hole 30 is formed along the front and rear directions of the swing cams 7 and 7, and the tip opening 30a is formed so as to face the cam surface 7a. Is formed in a range that does not abut.
[0064]
Therefore, according to this embodiment, the lubricating oil collected in the collecting hole 30 from the oil reservoir 22 at the time of swinging of the swing cams 7, 7 is directly jumped up in the direction of the pin 20, and By sufficiently lubricating around 20, the same operation and effect as in the above embodiments can be obtained.
[0065]
In addition, since the lubricating oil in the collecting hole 30 is also supplied into the pin hole 7c at the same time, the lubricating oil is sufficiently supplied between the pin hole 7c and the pin 21 so that both pin 20 , 21 around.
[0066]
FIG. 9 shows a still further example, in which the basic configuration of the collecting recesses 12, 12, etc. is the same as that of the first embodiment, but is characterized by both ends 15a, 15b of the link rod 15 and the rocker arm. The gaps 31 and 32 are formed between the other end 13b of the thirteen and the connecting portion between the swing cam 7 and the other end.
[0067]
Therefore, the lubricating oil collected by the collecting recesses 12 and 12 is jumped up by the swing of the swing cams 7 and 7 or is transmitted along the outer surface of the swing cams 7 and 7 to the lubricating oil. The liquid is supplied into the gaps 31 and 32 and is held therein. For this reason, it becomes possible to lubricate both pins 20 and 21 more stably and continuously.
[0068]
Further, as another embodiment, the upper surface 7d is simply formed flat without forming an uneven portion on the cam nose portion 7b side of each of the swing cams 7, and when the swing cam 7 swings, The lubricating oil in the oil reservoir 22 can be scooped up by the simple upper surface 7d.
[0069]
According to this embodiment, the lubricating oil in the oil reservoir 22 can be actively scooped up by the flat upper surface 7d of the swing cam 7, so that the lubricating oil O is supplied more around the pins 20, 21. In addition to the above, the manufacturing operation is facilitated because no concave and convex processing is required.
[0070]
The technical ideas other than the claims that can be grasped from the embodiment will be described below.
4. A valve gear for an internal combustion engine according to claim 3, wherein a concave portion is formed on an upper surface of the swing cam on a cam nose portion side.
[0071]
Therefore, a large amount of lubricating oil in the oil reservoir can be collected in the concave portion, so that more lubricating oil can be supplied to the pivot.
(B) A gap is formed between the swing cam and a link member of a transmission mechanism connected to the swing cam via a pivot. Of the internal combustion engine.
[0072]
Therefore, the lubricating oil can be held between the rocking cam and the link member as well as the lubricating oil can be positively supplied to the pivot portion located above with the rocking of the rocking cam. Lubricating oil can be sufficiently supplied also to a pivot portion located below which is a connecting portion between the swing cam and the link member.
(C) A concave and / or convex portion is provided on the side surface of the swing cam, and the concave or convex portion is immersed in the lubricating oil in the oil reservoir when the swing cam lifts the engine valve to the maximum. The valve train for an internal combustion engine according to claim 1, wherein the valve train is configured as follows.
[0073]
Therefore, even if the cam nose portion of the swing cam is not sufficiently immersed in the oil reservoir, the lubricating oil sufficiently adheres to the concave and convex portions on the side of the swing cam, so that a large amount of lubricating oil is supplied to the pivot portion. can do.
(D) The oscillating cam is provided with a communicating portion that communicates from the portion immersed in the oil reservoir to the pivot when the oscillating cam lifts the engine valve to the maximum. The valve train for an internal combustion engine according to claim 1.
[0074]
Since the lubricating oil in the oil reservoir is guided and supplied to the pivot from the part immersed in the lubricating oil through the communicating portion, the supply of the lubricating oil to the pivot is further increased, and the lubrication performance is further improved. .
(E) The support shaft is constituted by a drive shaft to which torque is transmitted from a crankshaft of the engine, and an eccentric drive cam is fixed to the outer periphery of the drive shaft, while the transmission mechanism is fixed to the outer periphery of the control shaft. The rocker arm is swingably supported on the outer peripheral surface of the eccentric control cam, and has one end linked to the drive cam via a link arm, and one end rotatably connected to the other end of the rocker arm via a pin. A link rod rotatably linked to the swing cam via a pin via a pin, and controlling the rotation of the control shaft and the control cam in accordance with an engine operating state, thereby controlling the rocker arm. 2. The valve operating apparatus for an internal combustion engine according to claim 1, wherein a valve lift amount of the engine valve is changed by changing a swing fulcrum and changing a sliding position of the swing cam with respect to the engine valve. .
[0075]
The present invention is not limited to the configuration of each of the above-described embodiments, and can be applied not only to the intake valve side but also to the exhaust valve side. It is also possible to apply to a valve train.
[Brief description of the drawings]
FIG. 1 is a sectional view showing a first embodiment of a valve train according to the present invention.
FIG. 2 is a perspective view showing a variable mechanism provided in the embodiment.
FIG. 3 is a plan view of the valve train according to the embodiment.
FIG. 4 is a perspective view showing one swing cam provided in the present embodiment.
FIG. 5 is a perspective view showing one swing cam provided in the second embodiment.
FIG. 6 is a perspective view showing one swing cam provided in a third embodiment.
FIG. 7 is a perspective view showing one swing cam provided in a fourth embodiment.
FIG. 8 is a perspective view showing one swing cam provided in a fifth embodiment.
FIG. 9 is a plan view of a valve train according to a sixth embodiment.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Cylinder head 2 ... Intake valve 3 ... Drive shaft 4 ... Camshaft 7 ... Swing cam 8 ... Transmission mechanism 9 ... Variable mechanism 12 ... Collection recess 13 ... Rocker arm 14 ... Link arm 15 ... Link rod 20 ... Pin (Pivot)
21 ... Pin (Pivot)
22 oil reservoir 23 first oil passage 24 second oil passage 27 concave 28 concave 29 convex 30 collecting hole (communication part)
31 ・ 32… Gap

Claims (3)

A swing cam that is swingably provided on the support shaft and swings to open and close the engine valve;
A pivot portion provided on the swing cam at a position separated from the support shaft;
A transmission mechanism rotatably connected to the swing cam via the pivot portion,
A valve gear for an internal combustion engine that opens and closes an engine valve by swinging the swing cam by a driving force transmitted to the transmission mechanism,
An oil reservoir is provided at a predetermined position within a range in which the swing cam of the cylinder head swings, and when the swing cam swings, lubricating oil in the oil sump attached to the swing cam is moved toward the pivot support portion. A valve train for an internal combustion engine, wherein the valve train is configured to jump up. The internal combustion engine according to claim 1, wherein the swing cam is disposed such that a tip end of a cam nose portion of the swing cam is immersed in the oil reservoir when the engine valve is lifted to a maximum. Engine valve gear. The upper surface of the oscillating cam on the cam nose portion side is formed in a flat shape, and when the oscillating cam oscillates, the flat upper surface is configured to scoop up the lubricating oil in the oil reservoir. Item 3. A valve train for an internal combustion engine according to item 1 or 2.

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